Multiple pump



Dec. 18, 1.945.

L. BEEH MULTIPLE PUMP Filed July 4, 1944 4 Sheets-Sheet 1 Z7 Z8 5/ 54 L BY /fm 5M Dec. 18, 1945. L'. BEI-:H 2,391,221

' MULTIPLE PUMP l Filed July 4, 1944 v 4 sheets-sheet 2 INVENTOR.

' LOU/ 5 BEE H a a/ 58 Arran/VFY Dec. 18, 1945. L. BEEH l 2,391,221

MULTIPLE PUMP Filed July 4, 1944 4 sheets-sheet s z/s za 39 gb l N VEN TOR.

Dec. 18, 1945.

L. BEEH MULTIPLE PUMP Filed July 4, 1944 IZZ.

4 Sheets-Sheet 4 INVENToR.' LOU/.S BE E H I sure type with sparkignition.

Patented Dec. 18,-1'1945l UNITED 4STATES PATENT oFFlcE Louis Beek, liong Meadow, Mass. `Application 4, 1944, Serial No. 543,445

iol. s-6) 9Claims.

The invention relates to a multiple pump for two media. such as the fuel and lubrication oil .of internal combustion engines, and it contemplates the provision of a pump of that kind which is particularly well suited for use, e. g. as an inJection pump for engines of the constant-pres- The invention also aims to provide a combinedfuel and oil pump of relatively simple structure wherein the pressure oil delivered may be utilized, on the one hand, to lubricate the movable parts of the pump and, if so desired, also of extraneous devices, and on the other hand, to serve as a working medium in a device controlling the injection of fuel delivered by the pump to a cylinder or a plurality of cylinders of an engine to which the pump may be connected'. According to the further invention, such controlling device may be rendered responsive to the vacuum prevailing in the manifold of such ,engine in order to adjust the quantity of fuel delivered to the engine cylinders.

The invention mainly consists in the combination of a pump of the rotary vane type with a plunger pump of the reciprocating type wherein a spring-biased plunger is shiftable in a radial cylindrical chamber of the rotor-and both the fluid-propelling elements, i. e. the vane-like element and the plunger engage each other so as to mutually cooperate, the one in transmitting driving motion to the other. In the preferred form for use with multiple cylinder engines both the rotary pump and the reciprocating plunger pump parts comprise a plurality of nuld propel- .ling members, that means Ithere are a plurality of plungers operating in as many cylindrical chambers respectively of the rotor to pump fuel and there are also as many vane-like members 'operating in one stationary pumpeccentrically arranged in relation to the rotor chamber or operating-in a plurality of such chambers one Aafter the other in order to pump oil, wherein,

however, the number of-pump chambers of the.

one kind need not be the same as that of the other kind. In a modified form of the invention, the pump part comprising the reciprocating plungers may be used as the oil pump, whereas the part vcomprising the vane-like elements may constitute the fuel pump. Further, according to the invention the-delivery of the pumped fuel occurs from a pressure chamber through a plurality of ports, as many as there are cylinders of the engine to be charged by the pump, and these ports are controlled by a piston-like valve rotating with the pump rotor and subjected to a pressure difference of the fuel and 'oil in order to meter the quantity oi' fuel ejected through the ports. The invention also consists of means whereby the valve may respond to changes in the vacuum prevailing in the manifold of a ma- .chine to which the pump is attached. Other means may be provided in Vorder to utilize the pumped oil for lubricating movable parts of the pump and/or extraneous parts. and also means to prevent the fuel pressure andthe oil pressure from rising beyond a predetermined maximum.

Further objects and details of the invention will be apparent from the description given hereinafterand the accompanying drawings illustraty alongone ofthe rotor plungers is shown having its axis coincident with the plane of the cross-section;

l Fig. 10 is a longitudinal cross-section of another embodiment and Fig. l1 is a diagrammatical, longitudinal-crosssection of a portion of another embodiment for use as a two-stage pump for only one medium.

Referring now. tothe drawings, the embodiment of Figs. 1 to 9 comprises a housing II consisting mainly of three coaxial parts I2,I3, Il

held together by means such as screw bolts I5 and IS respectively. Parts I2 and I3 enclose a cylindrical space Il formed by a disc-like portion I8 of part I3 and a .disc-like portion I9 and a. ring-shaped wall 20 of part I2. This space is lined by a lower plate 2l, an upper plate 22 and a. ring 23, the plates and the ring being'secured by the aforementioned bolts I5 against any movement in relation to the housing. -In- `teriorlyof the members 2I te 23 a .disc-shaped rotor 24 is rotatable, the lower shaft portion 25 of which is journaledin a sleeve-likeportion 26 of the housing and projects therefrom so that it may be connected with an extraneous driving element (not shown) for rotation, whereas the uP- per shaft end 21 of the rotor has its bearing in a tubular extension 28 of the plate 22. The ring 23 is interiorly so shaped as to form together with the rotor 24 and the plates 2| and 22, the4 chamber or 'plurality of chambers` ol' the rotary pump part of the device. As stated hereinbefore,

the number of said chambers may be 4selected according to the requirements in each case. In.

Plunger 32 is biased by a spring 34 between the bottom of its 'cylinder chamber 3| and the plunger 32. In Fig. 3, a plunger 32 with spring 34 is shown in only one of the chambers 3| in order to avoid overcrowding of the figure, and to `show more clearly certain ports in the cylinders which will be described hereinafter. Vane-like elements are provided in order to propel uid through the chambers 28 and 30 when the rotor rotates. I have found that particularly ,good results can be obtained if these elements are in the formr of'rollers. Such rollers 35 are interpositioned between the inner wall vof ring 23 and the upper ends of the plungers 32 so thateach associated spring 34 tends to urge the roller against ring 23. On the other hand,.if the rotor rotates,

the inner wall or ring 23 will urge a roller approaching the narrow portion of; the ring Space towards the rotor axis, thereby pushing the plunger 32 in the same direction against the restraint of the spring 34. In order to make such movement of'the roller possible, the side wall of the rotor is provided with slots 36 which serve to guide the rollers in radial direction with respect,

to the rotor.

Inlet ports and outlet ports are lprovided in y the various chambers and conduits are provided .in order to convey fiuid to and from the rotary pump part as well as to and from the plunger pump part. In the embodiment of Figs. 1 to 9 fuel is to be delivered by the plunger pump apart;

whereas the rotary pump part is used to deliver oil for lubricating purposes of the various movable members of the device and also for the purpose of controlling the delivery of fuel toan extraneous machine. For this purpose the housing has a lateral miet socket a1 which communicates with parison of Figs. 2 and 4. Slots 43 are in communication with anv lannular space 44 formed between the housing part I3 and the tubular extension 28 ofthe plate 22. Now it will be clear that fuel entering from the socket 31 will fill the conduits 38 and slots 48 to enter the bore v4| of each cylinder 3| which during the rotation of rotor 24 happensto be in a position in which the bore 4| registers with a slot 40. On the other hand, when a chamber 3| is in a position in which its bore 42 registers with one of the slots 43 fuel may be expelled from that chamber 3| into the ring space 44. Ring space 44 opensinto cylinder chamber 45m whicha plunger-like slide valve4'6" is movable in axial and 'peripheraldirections'.-4

lI he slide valve has a tapering groove 41 in its.l

side wall to control by its movement aplurality oi' outlet ports 48 provided in the wall of the housing part I3,- so that fuel from the space 44 and chamber 45 can be discharged -through the outlet ports 48 in accordance with a movement of the valve 46. Preferably there are as many outlet ports 48 as there are cylinders in the engine to be charged by the pump. Each outlet port may also be equipped with a check valve 49 `as clearly shown in Fig. 1.vv The number of outlet ports 48 may differ from that of the pump chambers 3| in the rotor. However. the fuel pump parts should be so dimensioned that they discharge into space 44, per each rotor revolution, al quantity of fuel not less than the maximum total which may be I required to be discharged through the ports 48.

In order to prevent the occurrence of excessive pressure a relief valve 50 may be located in the housing part I3 so as to connect space 44 with inlet conduit 38 through openings 5| and 52 of the valve chamber 53 when the valve member or ball 54 is raised from its'seat against therestraint of spring 55.

Another socket 56 is in communication with an arcuate conduit 51 in the housing part I2 and endingfin two diametrically opposite slots 53 of disc plate 2| underneath they crescent-shaped chambers v28 and 38 respectively of the rotary pumppart, as shown in'Figs. 2 and 3. Angularly spaced from the slots 58 are outlet slots 58 in the upper plate 22 (Fig. '4). 'Ihe slots 59- communicate each with a' conduit 60 (Figs. l and 9) extending to the top of chamber 45 so as to4 ll that chamber on top of thek plunger valve 46 except for the space taken byA an additional member to be ydescribed hereinafter.v From the foregoing it will be clear that upon rotation of the rotor taking along the rollers 35, oil may be 'sucked through the inlet 56 and'slots 58 into the pump chambers29 andv 30 to be pressed out through slots 58 and conduits 60, thereby filling the upper portion of chamber 45 and subjecting the plunger valve to the pressure difference of the oil on vtop and they fuel beneath it. In addition to groove 41, a helical groove 6| is provided on the outer wall of the plunger 46 yand in communication with the upper part of chamber 45 through an opening 62. The lower endof the groove 6| ends in a radial bore 63 which communicates with a central bore 64 of a lower extension 660i' thev plunger and in continuation thereof with-an axial bore 66 of the rotor shaft 25. By means ofa radial bore 61, a groove 68 longitudinally of the shaft 25 and a cross bore y 68 in the housing, oil from the upper portion of chamber 46 may reach a vrelief -valve 18 in the housing part 2 in order to return oil to the inlet conduit 614 when the -oil pressure reaches a predetermined height. It will be clear that the groove mayl serve not only as a conduit to the last mentioned valve, but also to lubricate the lower bearing of the shaft in thehousing portion 26. Similarly, branch gro'oves 1| and 12in connection with the bores 64 and 66 may :be provided for the upper bearing of the rotor shaft and for the extension 65 of plunger 46 which is in a splined connection with the rotor shaft as will be explained hereinafter. Other oil grooves may be' provided to lubricate the contacting surfaces of the rotor 24 and the plates 2| and 22. For this purpose, plate 2| has on its upper side a plurality of arcuate grooves 14 each with a radial branch 16 extending to the yperiphery of tlie plate so as -to communicate with the pump chambers 23 and 36` respectively. :Similar oil grooves 'I6 with radial branchesl 11 may be worked in-the'lower side of` the lplate 22. Cross bores 18 are provided in the rotor through the cylinders 3| in such a position that they may register with the arcuate slots 14 and 16 and the radius of these slots and the location ofthe bores 18 are such that oil may enter into the annular space formed by the recessed portions 33 of the piston 32 in the chambers3l. It has been stated hereinbefore that the relief valve will open under a certain pressure. This pressure will be so selected that correct functioning of the plunger valve 46 will |be insured while oil may circulate from the rotary pump part through the upper portion of chamber 45 and ybackagain to the oil inlet conduit 51 through the connecting conduits and valve 10. Inasmuch as, however, there is V a possibility of a dangerous super-pressure oc-l in registry with the outlet port. This dependscurring, another relief valve 19 may be provided and set to open at a higher pressure than valve 10 so as to act as a safety valve. Valve 19 is 'located in the interior of the rotor shaft 25 so that the oil pressure in conduit 66 bears thereon against the restraint of a spring 80 which is carried by a nut 8| screwed into the shaft 25 and which has an axial bore 82 through which valved oil can escape to the outside.

It has been stated hereinbefore that plunger valve 46 is in a splined connection with the upper portion 21 of the `rotor shaft. In fact, as clearly apparent from Fig. 5, the plunger extension 65 has a square cross-section and engages a correspondingly shaped axial bore 83 of the shaft. In consequence, plunger 46 will rotate together with the rotor and thereby connect the outlet ports 48 one after the other with the fuelillled chamber portion 45 in timed relation to lthe rotor rotation. The quantity Aof fuel-ejected through' each outlet 48 during one revolution depends upon the size of the cross-.section of the groove A41 which at the time of its passage is in turnl upon the vposition of thel plunger 46 in the axial direction of the chamber 45 and therefore, also -on the pressure dillerence of the fuel vand the oil in the opposite portions of the cham-v ber. In addition .,thereto'and according to the invention, the plunger position is rendered dependent on the pressure prevailing in the manifold of the engine to which the pump is applied.

`For this purpose the top portion I4 'of the h'ousing has an axial threaded bore 85 for connection to such manifold. Bore 85 opens into the ,interior of a'bellows 86 secured tothe lower side of portion I4 and the lower end of the bellows is secured to a plate 81 interiorly of the hollow'portion ofthe cup-shaped plunger 46. Interiorly of the bellows a compression spring 88 is positioned between plate 81 and the housing top I4, tending to urge plate 81 downward. An anti-friction bearing such as a. ball 89 is positioned between plate 81 and the bottom of plunger 46 so that the latter may rotate in relation to the belplunger 46 in chamber 45 depends on the one hand on the pressure difference between the fuel ered in accordance to the vacuum prevailing in the manifold of an engine.

In order to apply the pump according to the invention to an engine, the following connecand oil in chamber 45 as hereinbefore stated.

On the other hand, there acts upon the plunger the pressure of the spring minus the oil pressure on plate 81 and the vacuum of the manifold'. Thus, by properly selecting the forces of the spring of the relief valves 5|!v and 10 and of the spring 88, and properly dimensioning the crosssection of the groove 41\, a system can be attained in which the plunger position in chamber ,46 is such that desired quantities of -fuel will be delivtions are to be made: sockets 31 to a fuel source;

ports 48 with check valves 49 to the fuel inlet of the inlet ports 58 and the outlet ports 58 in relation to each other, the illustrated pump should turn in counterclockwise direction, indicated by the arrowainFig.2'.

The pump wil1 then operate as hereinafter described: Considering one of the rotor cylinders 3|, in a position in which its axis coincides with the radius 1 in Figs. 2 to 4, the relative position of the parts will then be that as shown' in Fig. 7. In this figure, the cross-section of the pump chamber 3|) covered by the pertaining rolle er 35 is very narrow and the roller proper is almost at the bottom of its slot 36 in rotor 24. The associated plunger 32 is almost in its farthest backward positiony in which, however, there is communication between the slot 4|) in the lower plate 2| and the 1ower portion of bore 4|, so

that. fuel may enter intothe chamber 3| from -the inlet conduit 39. The upper portion of bore 4I, however, is covered by the upper plate 22. The recess 33 of the plunger is just in front of the holes 18 so that oil present in the slots 14 of -the lower plate and slots 16 of the upper plate will get to the surface of the front portion of plunger 32. The space of the Achamber 38 will just begin to be connected to the oil inlet 58 (Fig. 2). because the roller preceding the one just contemplated will have advanced far enough so that the oil from port 58 may enter behind it. While the contemplated cylinder moves on during the rotation of the rotor, the oil in the,

chamber 30 between the roller of the contemplated lcylinder and the one forward of it will be propelled forward, some of it passing into the slots 14 and 16 through their radial branches 15 and 11 respectively. `When the axis of the contemplated cylinder coincides with the radius 8, the parts are in the position shown in Fig. 8 in which the oil inlet 58 is covered by the roller 35. Lubrication connection, however, exists between the plunger recess 33 and the lubricating grooves 14 and 16. In the meantime, the lower port 4| of the plunger chamber has been closed by the plate 2|, whereas the upper portion of the -bore 4| is in connection with the annular space 44 through the slot 4,3 of the -plate '22. It will be clear that on the way from the position 1 to 8 until the contemplated chamber 3| reaches the position of the topmost one in Fig. 3, the spring 34 via the' plunger 82 forces the roller 35 outside to contact the ring 23. through the next 90 of rotation, the roller will .force the associated plunger backward against the restraint of the' spring 84 owing to the eccentric shape of the ring 23. From the position in registry with radius 8 to and even beyond that of Fig. 9, theroller 35 will propel oil from the chamber 30 through the 'slot 58 (Fig. 9) into' the pressure of conduit 68.' Simultaneously, the

From there on,

plunger being shifted inward in chamber u wm Ahave reduced the volume of the latter and in view of the existing connectionbetween the upper partof the bore 4| with thev slot 43 in the top plate 22, while the lower portion of the bore 4| is closed by plate 2|, fuel will be expelled into the annular `space 44. A similar operation takes place in the other semi-circle owing to the presence of two symmetrically arranged pump chambers 30 and 28. Furthermore, since there are c shown live cylindrical chambers 3|. with plungers- 32 and rollers 35 each cycle.' i. e. one complete revolution of the rotor, includes the dei livery of ten equal part quantities of fuel to the ner, it takes along the plunger valve 46 as hereinbefore described. 'I'hereby the tapered slot 41 passes the fuel discharge ports 48 one after the other and permits a quantity of fuel under the pressure of the pump t escape through the ports and connected checkvalves 48 to charge the cylinders of the engine. The quantity of the fuel passing in each instant through a port 48 will depend on the one hand on the pressure prevailing in the annular space 44 and the lower portion of the chamber 45. If this pressure exceeds a predetermined maximum, relief valve 54 will open to permit some fuel to escape through the port 5| and to :Iiow back to the fuel inlet conduit 38. The quantity of fuel discharged through port 40 is-ffurther dependent on the size of the crosssection of the groove 41 passing the port 48 or in other words, it will be dependent on the axial position of the plunger 46. As hereinbefore described, the latter isv exposed to the pressure of the fuel in chamber 45 on the one hand and on the other hand to the oil pressure in the upper portion of chamber 45 which is charged with the oil pumped through the conduit 60. Furthermore, the plunger is loaded by spring 88 against the force of which a vacuum within the bellows as is acting wing to its connection to the manif old. Thus when the pump is operating luniformly the position of the plunger will essentially depend on the existing vacuum in the manifold, that means the lower the vaccum the higher will be the position of the plunger, so that more fuel will be discharged to the ports 48 if the vacug um becomes lower and that the quantity of fuel decreases when there is less vacuum prevailing within the bellows 86.

While thus fuel is discharged, lubricating oil pumped into the upper portion of chamber 45 passes through the helical groove 6| in the plunger surface. It will be noticed that during rotation of the plunger 46 the helical groove- 6| will hood of say 40 or 60 lbs. only. From groove 6I,

the oil ows on through the conduits 63, 64, 66, 61,68 to the relief or circulating valve 10 to return to the oil inlet conduit 51. The mentioned branch grooves such as 1|, 12 andthe lower por tion Yof the grooves 68 serve to lubricate the bearings of the rotating shaft 25 and the sliding surfaces between that shaft andthe plunger extension 65. If the pressure in the oil system exceeds a predetermined maximum, oil may escape through relief valve 18 and the bore 82.

' In the device just described, fuel is pumped 5 by a plurality of plungers operated in cylinders provided in a rotor, whereas lubricating oil is pumped by rollers operating in the manner of vanes in a rotary pump comprising mainly the said rotor with said rollers operating in an ec- -1o centric chamber. Now it will be clear that with certain modiflcations, it is also possible to use the rotary pump part to deliveriuel and the plunger pump part provided in the rotor to pump lubricatingioil. Further, the structure 4and arrangement of parts may -be modified by which an automatic adjustment of the control plunger position under the action of a vacuum in a manifold is attained. An example of such modifications is illustrated in the embodiment of Fig. 10.

20 In this embodiment the housing comprises the parts |0|, |02, |03 and |04 connected to each other by screw bolts some of which are indicated at |05 and |06. A rotor- |01 is arranged in the lower housing portion I0| *in a manner similar to that of Fig. l and the housing is provided with plates |08 and |09 between which the rotor is rotatable. There is further a ring IIO to form eccentric pump chambers I I with the rotors, and a' conduit |I2 permits fuel from the inlet II3 to enter chamber through a slot II4. Fuel may be discharged from this chamber II| through a slot or slots I I5v in the upper plate |09 of the annular chamber ||6 which is similar to the chamber 44 in the embodiment iirst described.

| I1 positioned between thering I I 0 and plungers IIB which are movable in radial chambers ||8 of the rotor. Chambers IIS serve as oil pump chambers with a conduit |20 conducting pumped oil to the upper portion of a chamber I 2| in which the control plunger |22 is axially movable. The latter issplined to the shaft |23 of the rotor so as to rotate with the latter but to be axially movable in the chamber I2|. The plunger is provided 45 with a. tapered groove |24 to control fuel discharge ports |25 as hereinbefore described with respect to the plunger |46. Interlorly of the plunger |22 a ball bearing |26 is arranged so as to-carry, non-rotatably with the plunger, a

connecting `1,rod.|21 which projects through the housing pai-t |03 forming the cover of chamber |2I. A spring |28 bears with its one end against the housing part |03 and with its other end on the bearing |26 so as to exert pressure on the lvalve ina direction opposite to that of the fuelfilled ring space II6. The upper end of the rod |21 is secured to the ycenter of a diaphragm |29 spanned between the housing portions |03 and |04 so as to form a vacuum chamber |30 with a socket |3| on its top for connection to the manifold of an engine. A

Now it will be clear that the embodiment of Fig. 10 operates' fundamentally in the same man ner as the embodiment of Fig. l with the difference, however, that the oil pumpv chambers are arranged interiorly of the rotor, whereas the fuel pumping elements are formed by the rollers guided in rotor I 01 in the chamber formed by the rotor land the surrounding eccentric ri-ng IIO.

The plunger |22 also is subject to forces of the .75 one side to the fuel and on the other side to the the upper plate 20|.

oil, both under pressure caused by the respective pumps. The oil circulating passages are also provided in amanner similar to that described, as a helical groove |32 in the plunger side connecting the upper portion of chamber |2| to an axial conduit |33 which in turn is connected to the oil inlet at |40. 'I'he operation of the pump' of Fig. 10 will -be understood without further explanation in view of what has been stated with reference tothe embodiment of Figs. l to 9.

In the foregoing it has been shown that the includingl side walls in huid-tight engagement pump according to my invention isv useful to deliver -simultaneously two different fluids. However, it is also possible to use the described pump for the purpose of acting on only one fluid in a two-stage compression if certain modiflcations are provided which mainly comprise a connection between the chambers of the one pump part and the other one. A pump thus modied may be employed for instance, for

charging an engine with kerosene which has certain lubricating qualities, so that no other lubricant is required for the movable parts 'of the pump. Fig. l1 illustrates the main portions of` such a pump wherein the rotary pump part constitutes the elements ,of the rst vthis pump, which comprises in an arrangement similar to that described hereinbefore, a housing 20| in which the rotor 202 is rotatable between the plates 203 and 204, and interiorly of the eccentric ring.205. The pump chamber 206 of the first stage is formed between the rotor and the ring 205. To this chamber the fluid may be admitted through an opening 201 with conduit 20,0l when the rollers 209 pass the port 2|0 in From chamber 208 the fluid will be expelled through opening 2|| and conduit2|2 so as to enter a receiving chamber 2|3 in the housing. From there the uid may enter the plunger chambers 2|! through ports 2li and 2|6 in plate 203 and rotor 202 respecftively when these ports are in registry. The iiuid entering the receiver 2| 3 is therefore compressed in the first stage and will then be further subjected to additional pressure by the plungers 2|1 until the ports 2|0 and'2l9 are in registry. If this occurs the fluid subjected to the second stage of compression lwill bev forced into the annular space 220 from where it may be ejected through a port 22| controlled by the groove 222 of the control plunger 223, in a manner more or less similar to that described with respect to the pumps of Figs. l and 10. It will be'noted that inthe caseof this modification no pressure fluid acts on the slide valve plunger223 from the top. In order to compensate for such lack of pressure from above,- a stronger spring 220 may be used in loading the plunger-so as to counteract vthe pressure in the space 220 to a desired degree.- O1' course, safety organsimay be applied to :permit back-flow from chamber 220 to receiver 2'|3 and also from the receiver 2|3 to the inlet 200. Such yorgans may be of 'a structure and arrangement similar to the valves 5I and 10 respectively,

and essence of my invention which for this rea.

with said rotor side walls respectively, a roller in engagement with said housing and guided-in radial slots provided in said rctor so as to be rotatable with thelatter, an inlet and an outlet port for one of said two iluids in saidhousing and under the control of said roller, .means to cause reciprocation of 'said roller radially in relation to said rotor, said means including a spring-biased plunger engaging said roller and tending to'urge it against said housing, said rotor being provided with a radial cylindrical chamber constituting a second pump chamber with said plunger'reciproeatable therein, an inlet port and an outlet port for the other one of said fluids in the rotor side walls respectively and in communication with said second pump chamber and orifices in the side walls of said housing so arranged as to communicate with said inlet and outlet ports respectively in predetermined angular positions of said rotor in relation to said housing. f

2. A combined pump for fuel and oil comprising a rotor including side walls, a housing for said rotor including an inner peripheral wall and side walls, said inner wall having a plurality of sections eccentric in relation tosaid rotor so as to form lwith the latter as many rst pump chambers as there are sections, said side walls being in fluid-tight engagement with the rotor side walls respectively, a plurality of Huid-propelling elements, the number of which may 'differ from that of said chambers, said elements being in engagement with the inner housing wall and said rotor and rotatable with the latter sor as to pass said iirst chambers one after the other, an

i inlet port and an outlet port for one of said fluids in each of said first chambers and under the control of the passing elements, a means for each of said elements to cause reciprocation thereof radially in relation to said rotor, each of said means including a spring-biasedplunger engaging the associated element and tending to urge it against said inner housing wall, said rotor being povided with a plurality of radial chambers, one for-each plunger and 'constituting sec- 0nd pump chambers, each of said second chambers having aninlet and an outlet port for the other one of said fluids in the rotor side walls respectively, as many inlet and outlet orifices as there are flrst chambers, said orices being so arranged as to register successively with said inlet and outlet ports for said other iluid respectively in predetermined positions ofthe rotor during its rotation.

3. A combined fuel and oil pump comprising a rotor including therein a radially arranged first pump part including an inner wall, a housing for said rotor and including an inner wall portion, means rotatable with said rotor and in Vshown in Fig. 1 with their accessories and conengagement with said inner wall, said means, said inner wall portion and said rotor constitut.`

ing asecond pump part, one of said pump parts being adapted. to pump. fuel, the other one to pump oil. a chamber provided in said housing in coaxial arrangement with said rotor so as to receive fuel from the fuel pump part, a slide valve in Said chamber in rotatable connection with said rotor so as to control an `outlet oriilce in the wall oi' said chamber, and ducts in the housing to conduct oil from the movable members of the device.

4. A combined pump for fuel and oil comprising a rotor including therein a radially arranged first pump part, a housing for said rotor and including an inner wall portion, means rotatable with said rotor and in engagement with said inner wall portion, said means. said inner wall portion and said rotor constituting a second pump part, one oi which parts being adapted to pump fuel, the other one to pump oil, a cylindrical chamber provided in said housing in coaxial arrangement with said rotor, conduits from said pumps tothe opposite chamber end portions respectively, an outlet from said chamber intermediate its ends, relief valves in communication with said chamberpcrtions respectively. a plunger valve in said chamber so as to be exposed on its opposite sides to the fuel and oil pressures prevailing in said chamber portions respectively. said plunger being rotatable with `said rotor and movable in axial direction and being provided with a tapering groove in its side v wall so as to control said outlet according to the rotor. rotation and in response to differences of the fuel and oil pressures and to connect said outlet r temporarily with the chamber portion connected lto said .fuel pump part.

5. A combined pump for fuel and oil comprising a rotor including therein a radially arranged rst pump part, a housing for said rotor and including an inner wall portion, means rotatable with said rotor and in engagement with said inner wall portion, said means, said inner wall porrtion and said rotor constituting a second pumpl part, one of saidparts'being adapted to pump fuel, the other one to pump oil, a cylindrical y chamber provided in said 'housing in coaxial arrangement with said rotor, conduits from said pumps to the opposite chamber end portions respectively, and outlet from said chamberv intermediate its ends, a first relief valve in communication with the chamber 'portion connected to 4 the fuel pump part, a second `and a third relief valve in communication with the chamber nor-v oil Pump part tothe asomar able in axial direction and being provided with a tapering groove in its side wall so as to convtrol said outlet according to'- the rotor rotation and in response to differences of the fuel and oil pressures and to connect said outlettemporarily with the chamber portion connected to said fuel pump part. v

6. A pump as claimed in claim 5, said plunger being provided with a substantially helical lubricating groove inits side wall, and said groove constituting a portion of the connection between said second and third relief valves and the chamber portion connected tosaid oil pump.

7. A combined fuel and oil pump comprising two parts, one adapted to pump fuel, the other one to pump oil, a substantially cylind-rical housing with a plurality of ports in its side wall, a slide valve rotatable and axially shiftable in said housing and dividing the latter in a first and a second chamber, said valve being a means to connect one of said ports after the other to said first chamber and to meter the ilow through said ports according to -its axial position, resilient means in engagement with said housing and said valve pump part to said first chamber, and a second tionwconnected to the oil pump part, saidsecond relief valve opening towards an inlet to the oil pump part. said third relief valve being adjusted to open towards the outside under a higher pres.-

sure than said second relief valve, a. plunger valve in said chamber so, as to be exposed on its opposite sides to the fuel and oil pressures prevailing in said chamber portions respectively; said plunger being rotatable vwith said rotor and movcate the latter.

conduitfrom the pressure side of the oil pump part to said second chamber.

8.'A combined fuel and oil pump comprising two parts, one adapted to pump fuel, the other one to ypump oil,'and including a rotatable shafted pumping member, a substantially cylindrical housing coaxial with said member and having a plurality 'of vports in'its side wall, a slide valve in said housing and connected for common rotation with said member but being axially shiftable, said valve being a means to connect one of said ports after the other to said first chamber and to meter the now through said ports according to its axial position, resilient means in engagement with said housing and said valve so as to bias the latter in one axial direction, a rst conduit from the pressure side of said fuel pump part to said first chamber, a second conduit from the pressure' side of .the oil pump part to said secondvchamber, an axial discharge conduit in said member including its'shaft, and a duct in said valve connecting saidv second chamber to said discharge conduit. g

9. A pump as claimed in claim 8 further comprising branch conduits of said discharge conduit tothe movable parts of the pump to lubri- LOUIS BEEH. 

